US20150323007A1 - Half bearing - Google Patents
Half bearing Download PDFInfo
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- US20150323007A1 US20150323007A1 US14/409,388 US201314409388A US2015323007A1 US 20150323007 A1 US20150323007 A1 US 20150323007A1 US 201314409388 A US201314409388 A US 201314409388A US 2015323007 A1 US2015323007 A1 US 2015323007A1
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- United States
- Prior art keywords
- sliding layer
- sliding
- half bearing
- oil
- layer
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Links
- 239000012791 sliding layer Substances 0.000 claims abstract description 82
- 238000005299 abrasion Methods 0.000 claims abstract description 28
- 239000000463 material Substances 0.000 claims abstract description 28
- 239000010410 layer Substances 0.000 claims abstract description 26
- 239000011347 resin Substances 0.000 claims abstract description 20
- 229920005989 resin Polymers 0.000 claims abstract description 20
- 239000000956 alloy Substances 0.000 claims abstract description 18
- 229910045601 alloy Inorganic materials 0.000 claims abstract description 17
- 239000002184 metal Substances 0.000 claims abstract description 15
- 229910052751 metal Inorganic materials 0.000 claims abstract description 15
- 239000000758 substrate Substances 0.000 claims abstract description 15
- 229920001343 polytetrafluoroethylene Polymers 0.000 claims abstract description 14
- 239000004810 polytetrafluoroethylene Substances 0.000 claims abstract description 14
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical class [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 claims abstract description 12
- -1 polytetrafluoroethylene Polymers 0.000 claims abstract description 12
- 229920000049 Carbon (fiber) Polymers 0.000 claims abstract description 9
- 239000004917 carbon fiber Substances 0.000 claims abstract description 9
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims abstract description 9
- 230000003746 surface roughness Effects 0.000 claims description 21
- 239000002245 particle Substances 0.000 claims description 7
- 238000005245 sintering Methods 0.000 claims description 6
- 238000005461 lubrication Methods 0.000 abstract description 4
- 238000001000 micrograph Methods 0.000 description 9
- 239000010949 copper Substances 0.000 description 7
- 238000005422 blasting Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 229910052802 copper Inorganic materials 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000007599 discharging Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000000654 additive Substances 0.000 description 1
- 230000000996 additive effect Effects 0.000 description 1
- 230000008034 disappearance Effects 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B22—CASTING; POWDER METALLURGY
- B22F—WORKING METALLIC POWDER; MANUFACTURE OF ARTICLES FROM METALLIC POWDER; MAKING METALLIC POWDER; APPARATUS OR DEVICES SPECIALLY ADAPTED FOR METALLIC POWDER
- B22F7/00—Manufacture of composite layers, workpieces, or articles, comprising metallic powder, by sintering the powder, with or without compacting wherein at least one part is obtained by sintering or compression
- B22F7/06—Manufacture of composite layers, workpieces, or articles, comprising metallic powder, by sintering the powder, with or without compacting wherein at least one part is obtained by sintering or compression of composite workpieces or articles from parts, e.g. to form tipped tools
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/20—Sliding surface consisting mainly of plastics
- F16C33/203—Multilayer structures, e.g. sleeves comprising a plastic lining
- F16C33/206—Multilayer structures, e.g. sleeves comprising a plastic lining with three layers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/0804—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B27/0821—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block component parts, details, e.g. valves, sealings, lubrication
- F04B27/086—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block component parts, details, e.g. valves, sealings, lubrication swash plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/046—Brasses; Bushes; Linings divided or split, e.g. half-bearings or rolled sleeves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/20—Sliding surface consisting mainly of plastics
- F16C33/201—Composition of the plastic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2253/00—Other material characteristics; Treatment of material
- F05C2253/12—Coating
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2253/00—Other material characteristics; Treatment of material
- F05C2253/20—Resin
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/02—Plastics; Synthetic resins, e.g. rubbers comprising fillers, fibres
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
- F16C2208/20—Thermoplastic resins
- F16C2208/30—Fluoropolymers
- F16C2208/32—Polytetrafluorethylene [PTFE]
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2220/00—Shaping
- F16C2220/20—Shaping by sintering pulverised material, e.g. powder metallurgy
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/54—Surface roughness
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/20—Application independent of particular apparatuses related to type of movement
- F16C2300/28—Reciprocating movement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/44—Centrifugal pumps
Definitions
- the present invention relates to a half bearing which slidably bears a member to be slid.
- a sliding material As the sliding member constituting a bearing, a sliding material has been known in which a porous layer composed of a copper (Cu) series alloy is formed on a metal substrate and resin materials mixing polytetrafluoroethylene (PTFE) and lead (Pb) coats this porous layer.
- Cu copper
- PTFE polytetrafluoroethylene
- Pb lead
- Such a sliding material in which a sliding layer is formed by the resin materials has excellent slidability but causes large abrasion loss, which is not suitable for usage under a heavy load condition. Since the usage of Pb is being limited, any sliding material free from Pb has been developed.
- a sliding material in which Cu series alloy is stuck to a metal substrate has been also known.
- the sliding material in which Cu series alloy is stuck to the metal substrate such as copper plated steel plate and the like has less slidability than that of a sliding material in which a sliding layer is formed by any resin materials but is capable of preventing abrasion.
- a technology to accelerate a formation of oil film by forming on a surface of the sliding layer any uneven shapes for oil reservoir has been proposed.
- Patent Document 1 Japanese Patent Application Publication No. 2006-226299.
- the invention has an object to present a half bearing that has an excellent abrasion resistance, and surely forms an oil film under boundary lubrication in which it is difficult to form any oil film.
- the invention relates to a half bearing containing a porous layer composed of Cu—Sn series alloy, which is formed on a surface of a metal substrate, and a sliding layer in which the porous layer is covered with resin material including at least polytetrafluoroethylene and a carbon fiber, wherein an uneven surface which maintains oil to form an oil film and has a height that maintains the oil so that the oil film is formed against abrasion when a member to be slid is sliding, is formed on a surface of the sliding layer slidably bearing the member to be slid, and the half bearing is formed on a circular arc along a direction in which the member to be slid swings.
- the uneven surface of the sliding layer prefferably has surface roughness of 3.0 through 10.0 ⁇ m in arithmetic mean roughness (Ra). Further, it is desirable to form the porous layer by sintering Cu—Sn series alloy having a particle size of 45 through 250 ⁇ m, the particles thereof being dispersed over a surface of the metal substrate, and to form the sliding layer by impregnating the resin material including at least the polytetrafluoroethylene and the carbon fiber into the porous layer by a roller having uneven surface for transferring the uneven surface on the sliding layer and sintering them.
- the half bearing according to the invention by forming the uneven surface which maintains the oil to form an oil film and has a height that maintains the oil so that the oil film is formed against abrasion when a member to be slid is sliding, on a surface of the sliding layer slidably bearing the member to be slid, it is possible to form the oil reservoir on the surface of the sliding layer and to maintain the uneven shape on the surface of the sliding layer even under use conditions such that heavy load is applied.
- FIG. 1 is a perspective view of a half bearing according to an embodiment of an invention for showing an example thereof.
- FIG. 2 is a sectional view of the sliding layer showing an example of the half bearing according to the embodiment thereof.
- FIG. 3 is a perspective view of the sliding layer in the half bearing according to the embodiment thereof for showing an example of a surface shape of the sliding layer.
- FIG. 4 is a diagram for showing a configuration example of a piston pump to which a sliding member according to the embodiment thereof is applied.
- FIG. 5A is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the embodiment.
- FIG. 5B is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the embodiment.
- FIG. 6A is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the comparison example 1.
- FIG. 6B is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the comparison example 1.
- FIG. 7A is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the comparison example 2.
- FIG. 7B is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the comparison example 2.
- FIG. 8 is a microphotograph of a surface of the sliding layer in the embodiment.
- FIG. 9 is a microphotograph of a surface of the sliding layer in the comparison example 1.
- FIG. 10 is a microphotograph of a surface of the sliding layer in the comparison example 2.
- FIG. 11 is a graph showing a variation in abrasion loss on each of the sliding layers of the embodiment and the comparison examples.
- FIG. 1 is a perspective view of the half bearing according to the embodiment of the invention for showing an example thereof.
- FIG. 2 is a sectional view of the sliding layer showing an example of the half bearing according to the embodiment thereof.
- FIG. 3 is a perspective view of the sliding layer in the half bearing according to the embodiment thereof for showing an example of a surface shape of the sliding layer.
- the half bearing 1 constitutes a bearing having a cylindrical shape as shown in FIG. 1 and an internal circumferential surface thereof is a sliding layer 2 with the member to be slid.
- the half bearing 1 is configured, as shown in FIG. 2 , so that a porous layer 4 composed of alloy material is formed on a surface of a metal substrate 3 , which is one surface thereof, and resin material 5 coats the porous layer 4 to form the sliding layer 2 .
- the half bearing 1 is provided with an uneven surface 6 on a surface of the sliding layer 2 which slidably bears the member to be slid.
- the uneven surface 6 is configured to have a shape that is suitable for forming an oil film and maintaining oil film and have the shape that prevents a variation of the shape by abrasion based on uneven loading by a swing of the member to be slid.
- the uneven surface 6 is configured to have a recess portion 6 a having a desired shape that becomes an oil reservoir in order to allow the oil film to be formed on a surface of the sliding layer 2 .
- the uneven surface 6 a is formed to have the reversed-quadrangular-pyramid shaped recess portions 6 a , in which line-like vertexes that are continuous are arranged in gridlike fashion.
- a height of the recess portion 6 a from a bottom thereof to a vertex thereof is provided on the basis of the abrasion loss in the sliding layer 2 and a surface roughness so that the recess portion 6 a can maintain a desired height is also provided.
- the porous layer 4 is formed by Cu—Sn series alloy.
- the porous layer 4 is formed by sintering Cu—Sn series alloy having a particle size of 45 through 250 ⁇ m, the particles thereof being dispersed over a surface of the metal substrate 3 so as to have a desired thickness.
- the sliding layer 2 is formed by the resin material 5 including at least polytetrafluoroethylene (PTFE) and a carbon fiber.
- the sliding layer 2 is formed by impregnating the resin material 5 into the porous layer 4 , which has been sintered on the surface of the metal substrate 3 , by a roller, not shown, having uneven shape for transferring the uneven surface 6 on the surface of the sliding layer 2 and sintering them.
- PTFE polytetrafluoroethylene
- the height of the recess portion 6 a from a bottom thereof to a vertex thereof is provided so that the uneven surface 6 of the sliding layer 2 has surface roughness of 3.0 through 10.0 ⁇ m, preferably 6.0 ⁇ m or more and 10.0 ⁇ m or less, in arithmetic mean roughness (Ra).
- the formation of the uneven surface 6 on the sliding layer 2 is done by transfer to the resin material 5 before the hardening thereof using a mold, it is easy to form the uneven shape having any desired height.
- the surface shape of the sliding layer 2 by configuring the surface shape of the sliding layer 2 to be the uneven surface 6 having a shape that is suitable for forming the oil film and maintaining the oil film and having the shape that prevents a variation thereof by abrasion based on the uneven loading by the swing of the member to be slid, it is possible to have an excellent abrasion resistance using polytetrafluoroethylene having low friction coefficient.
- the half bearing 1 according to the embodiment is preferably applicable to hydraulic equipment such as a hydraulic pump and the like.
- FIG. 4 is a diagram for showing a configuration example of the piston pump to which the half bearing according to the embodiment thereof is applied.
- FIG. 4 is a typical side sectional view thereof.
- a cylinder block 20 is attached to a case 30 with the input shaft 21 supporting it and driving force transmitted to the input shaft 21 forces the cylinder block 20 to rotate.
- plural cylinders 22 are formed along the rotation direction and a piston 40 is installed in each of the cylinders 22 so as to be freely drawn and inserted.
- the piston pump 10 is provided with a plain bearing 50 which rotatably supports the cylinder block 20 .
- the plain bearing 50 is provided with an inlet port 51 and an outlet port 52 which are opened along the rotating direction of the cylinder block 20 and is installed between the cylinder block 20 and the case 30 with the inlet port 51 and an inlet 31 provided in the case 30 being communicated to each other and the outlet port 52 and an outlet 32 provided in the case 30 being communicated to each other.
- the plain bearing 50 is configured so that when the cylinder block 20 rotates with it being pushed to an axis direction, the cylinder block 20 and the plain bearing 50 are relatively slid.
- the piston pump 10 is provided with a swash plate 60 for drawing and inserting the piston 40 in relation to each of the cylinders 22 of the cylinder block 20 together with the rotation of the cylinder block 20 , a yoke 61 for changing an angle of the swash plate 60 , and an operation piston 70 and a return spring 80 , which operate the swash plate 60 and the yoke 61 .
- the piston pump 10 together with the rotation of the cylinder block 20 , the cylinder 22 in which the piston is projected from the cylinder block 20 absorbs the oil but the cylinder 22 into which the piston is inserted from the cylinder block 20 discharges the oil.
- the piston pump 10 is configured so that, by changing an angle of the swash plate 60 and the yoke 61 , a stroke of the piston 40 alters and a discharged amount of the oil is adjustable.
- the piston pump 10 is provided with the half bearing 1 , which is attached to the case 30 , for swingably supporting the swash plate 60 and the yoke 61 .
- the half bearing 1 has the configuration described in relation to the above FIGS. 1 through 3 . By swing an axis portion 62 of the yoke 61 as the member to be slid with it being pushed to a circumferential direction, the axis portion 62 and the half bearing 1 are relatively slid.
- the piston pump 10 When the cylinder block 20 is configured to rotate in one direction, the piston pump 10 is configured so that the oil-absorbing side and the oil-discharging side are fixed but when the cylinder block 20 is configured to rotate in both forward and reverse directions, the piston pump 10 is configured so that the oil-absorbing side and the oil-discharging side are changeable.
- the cylinder block 20 slides in one direction or both forward and reverse directions along the circumferential direction while heavy load is applied thereto by pushing the cylinder block 20 to the axis direction. Accordingly, the cylinder block 20 and the plain bearing 50 slide in a circular direction with heavy load being applied to them.
- the piston pump 10 is also configured so that the swash plate 60 and the yoke 61 are swung in both forward and reverse directions to change a discharged amount of the oil.
- the half bearing 1 is configured so that the axis portion 62 of the yoke 61 slides on both forward and reverse directions along the circumferential direction while heavy load is applied thereto by pushing the axis portion 62 of the yoke 61 to the circumferential direction. Accordingly, the axis portion 62 and the half bearing 1 slide to a linear direction with heavy load being applied to them.
- the half bearing to be tested they prepared the half bearing 1 as the embodiment in which the porous layer 4 composed of Cu—Sn series alloy was formed on the surface of the metal substrate 3 , the resin material 5 including at least polytetrafluoroethylene and a carbon fiber coated the porous layer 4 to form the sliding layer 2 , and the uneven surface 6 was formed on the surface of the sliding layer 2 .
- the half bearing as the comparison example 1 in which the porous layer composed of Cu—Sn series alloy was formed on the surface of the metal substrate, and the resin material including polytetrafluoroethylene and lead (Pb) coated the porous layer to form a sliding layer 2 .
- the half bearing of the comparison example 1 no uneven surface was formed on the surface of the sliding layer.
- the sliding layer was formed by bonding plate-like Cu—Sn series alloy to the surface of the metal substrate, and the sliding surface having a predetermined surface roughness and a predetermined surface hardness was formed by performing shot blasting process on the formed sliding layer.
- Cycle Number 250 thousand cycles (ON 1 sec; OFF 1 sec);
- FIGS. 5A and 5B are graphs showing surface roughness shapes of the sliding layer before and after the test of the half bearing in the embodiment.
- FIG. 5A shows the surface roughness shape thereof before the test and
- FIG. 5B shows the surface roughness shape thereof after the test (250 thousand cycles).
- FIGS. 6A and 6B are graphs showing surface roughness shapes of the sliding layer before and after the test of the half bearing in the comparison example 1.
- FIG. 6A shows the surface roughness shape thereof before the test and
- FIG. 6B shows the surface roughness shape thereof after the test (250 thousand cycles).
- FIGS. 7A and 7B are graphs showing surface roughness shapes of the sliding layer before and after the test of the half bearing in the comparison example 2.
- FIG. 7A shows the surface roughness shape thereof before the test and
- FIG. 7B shows the surface roughness shape thereof after the test (250 thousand cycles).
- FIGS. 5A , 5 B, 6 A and 6 B are based on JIS B 0601 (1994).
- FIG. 8 is a microphotograph of a surface of the sliding layer after the test (250 thousand cycles) in the half bearing according to the embodiment.
- FIG. 9 is a microphotograph of a surface of the sliding layer after the test (250 thousand cycles) in the half bearing according to the comparison example 1.
- FIG. 10 is a microphotograph of a surface of the sliding layer after the test (250 thousand cycles) in the half bearing according to the comparison example 2.
- FIG. 11 is a graph showing a variation in the abrasion loss on each of the sliding layers of the embodiment and the comparison examples. The abrasion loss on each of the sliding layers of the embodiment and the comparison examples was obtained by measuring thickness of each of the half bearings before the test and thickness thereof for every cycle as the thickness after the test using a micrometer and calculating difference therebetween.
- the half bearing 1 according to the embodiment had the uneven surface 6 having a shape shown in FIG. 2 or the like on the surface of the sliding layer 2 , it indicated as shown in FIG. 5A that the arithmetic mean roughness (Ra) before the test was 6.018 ⁇ m, 10-point average roughness (Rz) before the test was 22.35 ⁇ m and average spacing in roughness (Sm) before the test was 0.4389 mm.
- the half bearing 1 according to the embodiment improves its heat resistant and its pressure resistant because the carbon fiber is mixed to the sliding layer 2 and prevents the abrasion of the sliding layer 2 as shown in FIG. 11 even under use conditions such that heavy load is applied for a long time. Further, since the half bearing 1 according to the embodiment has the uneven surface 6 , which is formed on the surface of the sliding layer 2 , having the height higher than that of each of the comparison examples shown in FIGS. 6A and 7A at initial stage as shown in FIG. 5A , the oil film is more surely formed so that they have found out that the shape of the surface of the sliding layer 2 in addition to the composition of the sliding layer 2 prevents the abrasion of the sliding layer 2 .
- the half bearing 1 prevents any abrasion of the sliding layer 2 because the sliding layer 2 is composed of polytetrafluoroethylene which has lower friction coefficient than that of Cu series alloy.
- the half bearing according to the comparison example 1 indicated as shown in FIG. 6A that the arithmetic mean roughness (Ra) before the test was 2.262 ⁇ m, the 10-point average roughness (Rz) before the test was 8.588 ⁇ m and the average spacing in roughness (Sm) before the test was 0.3299 mm.
- the half bearing according to the comparison example 1 As shown in the microphotograph of FIG. 9 , no adhesion was shown but the porous layer was exposed after 250 thousand cycles. They have found out that the half bearing according to the comparison example 1 has good slidability because lead (PB) is contained therein but the abrasion loss is large as shown in FIG. 11 so that there is a high probability of generating adhesion under use conditions in which that heavy load is applied for a long time.
- PB lead
- the half bearing according to the comparison example 2 indicated as shown in FIG. 7A that the arithmetic mean roughness (Ra) before the test was 2.299 ⁇ m, the 10-point average roughness (Rz) before the test was 8.798 ⁇ m and the average spacing in roughness (Sm) before the test was 0.3114 mm.
- any uneven shapes, which becomes the oil reservoir that forms the oil film remain, as shown in FIG. 5B , in the embodiment while any uneven shapes, which becomes the oil reservoir that forms the oil film, disappear, as shown in FIG. 7B , so that there is a high probability of generating the adhesion in the comparison example 2.
- the porous layer 4 in the half bearing 1 is preferably composed of Cu—Sn series alloy having a particle size of 45 through 250 ⁇ m, in order to maintain the sliding layer 2 under the use conditions such that heavy load is applied for a long time.
- the sliding layer 2 in the half bearing 1 is preferably composed of resin material 5 including the polytetrafluoroethylene which has low friction factor and a carbon fiber which has good heat resistant and good pressure resistant.
- the uneven surface 6 of the sliding layer 2 in the half bearing 1 preferably has surface roughness of 3.0 through 10.0 ⁇ m, more preferably, 6.0 through 10.0 ⁇ m, in the arithmetic mean roughness (Ra).
- the present invention is applied to a sliding member used under the boundary lubrication in which the heavy load is applied and it is difficult to form any oil film.
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Abstract
Description
- The present invention relates to a half bearing which slidably bears a member to be slid.
- As the sliding member constituting a bearing, a sliding material has been known in which a porous layer composed of a copper (Cu) series alloy is formed on a metal substrate and resin materials mixing polytetrafluoroethylene (PTFE) and lead (Pb) coats this porous layer.
- Such a sliding material in which a sliding layer is formed by the resin materials has excellent slidability but causes large abrasion loss, which is not suitable for usage under a heavy load condition. Since the usage of Pb is being limited, any sliding material free from Pb has been developed.
- As the sliding member constituting a bearing, a sliding material in which Cu series alloy is stuck to a metal substrate has been also known. The sliding material in which Cu series alloy is stuck to the metal substrate such as copper plated steel plate and the like has less slidability than that of a sliding material in which a sliding layer is formed by any resin materials but is capable of preventing abrasion. Further, a technology to accelerate a formation of oil film by forming on a surface of the sliding layer any uneven shapes for oil reservoir has been proposed.
- However, under a heavy load condition like an oil hydraulic pump called a piston pump, there has been a case when it cannot maintain such uneven shapes so that it cannot maintain desired slidability in usage for a long time.
- When increasing a height of the uneven shape, it is possible to avoid any disappearance of the oil reservoir by abrasion but it is difficult to form the uneven shape having a desired height on the surface of the sliding layer formed by the Cu series alloy.
- Accordingly, a technology to improve mechanical strength so that the sliding layer composed of the resin materials is not separated from porous layer by the sliding material in which the sliding layer is formed by any resin material and to form an oil reservoir having a desired shape have been known (For example, see Patent Document 1).
- In even the conventional sliding material, however, the mechanical strength of which is improved so that the sliding layer composed of the resin materials is not separated from the porous layer, it is impossible to sufficiently prevent abrasion loss under a heavy load condition and to maintain any desired slidability in usage for a long time, which may generate any adhesion.
- The invention has an object to present a half bearing that has an excellent abrasion resistance, and surely forms an oil film under boundary lubrication in which it is difficult to form any oil film.
- Inventors have found out that decreasing abrasion by an additive of resin materials constituting a sliding layer allows uneven shape on the sliding layer, which can form the oil film, to be maintained.
- The invention relates to a half bearing containing a porous layer composed of Cu—Sn series alloy, which is formed on a surface of a metal substrate, and a sliding layer in which the porous layer is covered with resin material including at least polytetrafluoroethylene and a carbon fiber, wherein an uneven surface which maintains oil to form an oil film and has a height that maintains the oil so that the oil film is formed against abrasion when a member to be slid is sliding, is formed on a surface of the sliding layer slidably bearing the member to be slid, and the half bearing is formed on a circular arc along a direction in which the member to be slid swings.
- It is desirable for the uneven surface of the sliding layer to have surface roughness of 3.0 through 10.0 μm in arithmetic mean roughness (Ra). Further, it is desirable to form the porous layer by sintering Cu—Sn series alloy having a particle size of 45 through 250 μm, the particles thereof being dispersed over a surface of the metal substrate, and to form the sliding layer by impregnating the resin material including at least the polytetrafluoroethylene and the carbon fiber into the porous layer by a roller having uneven surface for transferring the uneven surface on the sliding layer and sintering them.
- In the half bearing according to the invention, by forming the uneven surface which maintains the oil to form an oil film and has a height that maintains the oil so that the oil film is formed against abrasion when a member to be slid is sliding, on a surface of the sliding layer slidably bearing the member to be slid, it is possible to form the oil reservoir on the surface of the sliding layer and to maintain the uneven shape on the surface of the sliding layer even under use conditions such that heavy load is applied.
- This enables the oil film to be surely formed even under the boundary lubrication in which the heavy load is applied and it is difficult to form any oil film to decrease the abrasion. This also enables any heat generation to decrease so that it has excellent cavitation erosion resistance in an art of oil hydraulic machinery and thus, has an effect of preventing the sliding member from generating any adhesion.
-
FIG. 1 is a perspective view of a half bearing according to an embodiment of an invention for showing an example thereof. -
FIG. 2 is a sectional view of the sliding layer showing an example of the half bearing according to the embodiment thereof. -
FIG. 3 is a perspective view of the sliding layer in the half bearing according to the embodiment thereof for showing an example of a surface shape of the sliding layer. -
FIG. 4 is a diagram for showing a configuration example of a piston pump to which a sliding member according to the embodiment thereof is applied. -
FIG. 5A is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the embodiment. -
FIG. 5B is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the embodiment. -
FIG. 6A is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the comparison example 1. -
FIG. 6B is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the comparison example 1. -
FIG. 7A is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the comparison example 2. -
FIG. 7B is a graph showing a surface roughness shape of the sliding layer before and after the test of the half bearing in the comparison example 2. -
FIG. 8 is a microphotograph of a surface of the sliding layer in the embodiment. -
FIG. 9 is a microphotograph of a surface of the sliding layer in the comparison example 1. -
FIG. 10 is a microphotograph of a surface of the sliding layer in the comparison example 2. -
FIG. 11 is a graph showing a variation in abrasion loss on each of the sliding layers of the embodiment and the comparison examples. - The following will describe embodiments of a half bearing according to the present invention with reference to drawings.
FIG. 1 is a perspective view of the half bearing according to the embodiment of the invention for showing an example thereof.FIG. 2 is a sectional view of the sliding layer showing an example of the half bearing according to the embodiment thereof.FIG. 3 is a perspective view of the sliding layer in the half bearing according to the embodiment thereof for showing an example of a surface shape of the sliding layer. - The half bearing 1 according to the embodiment constitutes a bearing having a cylindrical shape as shown in
FIG. 1 and an internal circumferential surface thereof is asliding layer 2 with the member to be slid. The half bearing 1 is configured, as shown inFIG. 2 , so that aporous layer 4 composed of alloy material is formed on a surface of ametal substrate 3, which is one surface thereof, and resinmaterial 5 coats theporous layer 4 to form the slidinglayer 2. - The half bearing 1 is provided with an
uneven surface 6 on a surface of the slidinglayer 2 which slidably bears the member to be slid. Theuneven surface 6 is configured to have a shape that is suitable for forming an oil film and maintaining oil film and have the shape that prevents a variation of the shape by abrasion based on uneven loading by a swing of the member to be slid. - Namely, the
uneven surface 6 is configured to have arecess portion 6 a having a desired shape that becomes an oil reservoir in order to allow the oil film to be formed on a surface of the slidinglayer 2. In this embodiment, as shown inFIG. 3 , theuneven surface 6 a is formed to have the reversed-quadrangular-pyramid shapedrecess portions 6 a, in which line-like vertexes that are continuous are arranged in gridlike fashion. - Further, on the
uneven surface 6, in order to maintain the shape of therecess portion 6 a which is able to form the oil film even by the abrasion based on the swing of the member to be slid, a height of therecess portion 6 a from a bottom thereof to a vertex thereof is provided on the basis of the abrasion loss in the slidinglayer 2 and a surface roughness so that therecess portion 6 a can maintain a desired height is also provided. - In the half bearing 1, the
porous layer 4 is formed by Cu—Sn series alloy. Theporous layer 4 is formed by sintering Cu—Sn series alloy having a particle size of 45 through 250 μm, the particles thereof being dispersed over a surface of themetal substrate 3 so as to have a desired thickness. - In the half bearing 1, the
sliding layer 2 is formed by theresin material 5 including at least polytetrafluoroethylene (PTFE) and a carbon fiber. The slidinglayer 2 is formed by impregnating theresin material 5 into theporous layer 4, which has been sintered on the surface of themetal substrate 3, by a roller, not shown, having uneven shape for transferring theuneven surface 6 on the surface of the slidinglayer 2 and sintering them. - In the half bearing 1, the height of the
recess portion 6 a from a bottom thereof to a vertex thereof is provided so that theuneven surface 6 of thesliding layer 2 has surface roughness of 3.0 through 10.0 μm, preferably 6.0 μm or more and 10.0 μm or less, in arithmetic mean roughness (Ra). - As described above, since the formation of the
uneven surface 6 on the slidinglayer 2 is done by transfer to theresin material 5 before the hardening thereof using a mold, it is easy to form the uneven shape having any desired height. - In the half bearing 1 according to the embodiment, by configuring the surface shape of the sliding
layer 2 to be theuneven surface 6 having a shape that is suitable for forming the oil film and maintaining the oil film and having the shape that prevents a variation thereof by abrasion based on the uneven loading by the swing of the member to be slid, it is possible to have an excellent abrasion resistance using polytetrafluoroethylene having low friction coefficient. - Accordingly, in particular, the half bearing 1 according to the embodiment is preferably applicable to hydraulic equipment such as a hydraulic pump and the like.
FIG. 4 is a diagram for showing a configuration example of the piston pump to which the half bearing according to the embodiment thereof is applied.FIG. 4 is a typical side sectional view thereof. - In the
piston pump 10, acylinder block 20 is attached to acase 30 with theinput shaft 21 supporting it and driving force transmitted to theinput shaft 21 forces thecylinder block 20 to rotate. In thecylinder block 20,plural cylinders 22 are formed along the rotation direction and apiston 40 is installed in each of thecylinders 22 so as to be freely drawn and inserted. - The
piston pump 10 is provided with aplain bearing 50 which rotatably supports thecylinder block 20. Theplain bearing 50 is provided with aninlet port 51 and anoutlet port 52 which are opened along the rotating direction of thecylinder block 20 and is installed between thecylinder block 20 and thecase 30 with theinlet port 51 and aninlet 31 provided in thecase 30 being communicated to each other and theoutlet port 52 and anoutlet 32 provided in thecase 30 being communicated to each other. Theplain bearing 50 is configured so that when thecylinder block 20 rotates with it being pushed to an axis direction, thecylinder block 20 and theplain bearing 50 are relatively slid. - The
piston pump 10 is provided with aswash plate 60 for drawing and inserting thepiston 40 in relation to each of thecylinders 22 of thecylinder block 20 together with the rotation of thecylinder block 20, ayoke 61 for changing an angle of theswash plate 60, and anoperation piston 70 and areturn spring 80, which operate theswash plate 60 and theyoke 61. - In the
piston pump 10, together with the rotation of thecylinder block 20, thecylinder 22 in which the piston is projected from thecylinder block 20 absorbs the oil but thecylinder 22 into which the piston is inserted from thecylinder block 20 discharges the oil. Thepiston pump 10 is configured so that, by changing an angle of theswash plate 60 and theyoke 61, a stroke of thepiston 40 alters and a discharged amount of the oil is adjustable. - The
piston pump 10 is provided with the half bearing 1, which is attached to thecase 30, for swingably supporting theswash plate 60 and theyoke 61. The half bearing 1 has the configuration described in relation to the aboveFIGS. 1 through 3 . By swing anaxis portion 62 of theyoke 61 as the member to be slid with it being pushed to a circumferential direction, theaxis portion 62 and the half bearing 1 are relatively slid. - When the
cylinder block 20 is configured to rotate in one direction, thepiston pump 10 is configured so that the oil-absorbing side and the oil-discharging side are fixed but when thecylinder block 20 is configured to rotate in both forward and reverse directions, thepiston pump 10 is configured so that the oil-absorbing side and the oil-discharging side are changeable. On theplain gearing 50, thecylinder block 20 slides in one direction or both forward and reverse directions along the circumferential direction while heavy load is applied thereto by pushing thecylinder block 20 to the axis direction. Accordingly, thecylinder block 20 and theplain bearing 50 slide in a circular direction with heavy load being applied to them. - The
piston pump 10 is also configured so that theswash plate 60 and theyoke 61 are swung in both forward and reverse directions to change a discharged amount of the oil. The half bearing 1 is configured so that theaxis portion 62 of theyoke 61 slides on both forward and reverse directions along the circumferential direction while heavy load is applied thereto by pushing theaxis portion 62 of theyoke 61 to the circumferential direction. Accordingly, theaxis portion 62 and the half bearing 1 slide to a linear direction with heavy load being applied to them. - A test was carried out using the
piston pump 10 shown inFIG. 4 in order to inspect any influence in which a difference in configuration of the sliding layer and a shape of the surface thereof in the half bearing was exerted to durability such as the adhesion and the abrasion. As the half bearing to be tested, they prepared the half bearing 1 as the embodiment in which theporous layer 4 composed of Cu—Sn series alloy was formed on the surface of themetal substrate 3, theresin material 5 including at least polytetrafluoroethylene and a carbon fiber coated theporous layer 4 to form the slidinglayer 2, and theuneven surface 6 was formed on the surface of the slidinglayer 2. - Further, they prepared the half bearing as the comparison example 1 in which the porous layer composed of Cu—Sn series alloy was formed on the surface of the metal substrate, and the resin material including polytetrafluoroethylene and lead (Pb) coated the porous layer to form a sliding
layer 2. In the half bearing of the comparison example 1, no uneven surface was formed on the surface of the sliding layer. - Additionally, they prepared the half bearing as the comparison example 2 in which the sliding layer was formed by bonding plate-like Cu—Sn series alloy to the surface of the metal substrate, and the sliding surface having a predetermined surface roughness and a predetermined surface hardness was formed by performing shot blasting process on the formed sliding layer.
- Test condition was as follows:
- Cut-off durability test
- Discharge Pressure: 0 through 28 MPa;
- Cycle Number: 250 thousand cycles (ON 1 sec;
OFF 1 sec); - Temperature of Oil: 60° C.; and
- Number of Shaft Revolution N: 1800 rpm
-
FIGS. 5A and 5B are graphs showing surface roughness shapes of the sliding layer before and after the test of the half bearing in the embodiment.FIG. 5A shows the surface roughness shape thereof before the test andFIG. 5B shows the surface roughness shape thereof after the test (250 thousand cycles). - Further,
FIGS. 6A and 6B are graphs showing surface roughness shapes of the sliding layer before and after the test of the half bearing in the comparison example 1.FIG. 6A shows the surface roughness shape thereof before the test andFIG. 6B shows the surface roughness shape thereof after the test (250 thousand cycles). - Additionally,
FIGS. 7A and 7B are graphs showing surface roughness shapes of the sliding layer before and after the test of the half bearing in the comparison example 2.FIG. 7A shows the surface roughness shape thereof before the test andFIG. 7B shows the surface roughness shape thereof after the test (250 thousand cycles). Here,FIGS. 5A , 5B, 6A and 6B are based on JIS B 0601 (1994). -
FIG. 8 is a microphotograph of a surface of the sliding layer after the test (250 thousand cycles) in the half bearing according to the embodiment.FIG. 9 is a microphotograph of a surface of the sliding layer after the test (250 thousand cycles) in the half bearing according to the comparison example 1.FIG. 10 is a microphotograph of a surface of the sliding layer after the test (250 thousand cycles) in the half bearing according to the comparison example 2. Further,FIG. 11 is a graph showing a variation in the abrasion loss on each of the sliding layers of the embodiment and the comparison examples. The abrasion loss on each of the sliding layers of the embodiment and the comparison examples was obtained by measuring thickness of each of the half bearings before the test and thickness thereof for every cycle as the thickness after the test using a micrometer and calculating difference therebetween. - Since the half bearing 1 according to the embodiment had the
uneven surface 6 having a shape shown inFIG. 2 or the like on the surface of the slidinglayer 2, it indicated as shown inFIG. 5A that the arithmetic mean roughness (Ra) before the test was 6.018 μm, 10-point average roughness (Rz) before the test was 22.35 μm and average spacing in roughness (Sm) before the test was 0.4389 mm. - As opposed to such a shape before the test, it indicated as shown in
FIG. 5B that the arithmetic mean roughness (Ra) after the test under the above-mentioned condition was 3.491 μm, the 10-point average roughness (Rz) after the test was 12.74 μm and the average spacing in roughness (Sm) after the test was 0.4304 mm. - In the half bearing 1 according to the embodiment, as shown in the microphotograph of
FIG. 8 , a slight abrasion was shown on the vertexes of theuneven surface 6 on the surface of the slidinglayer 2 even after 250 thousand cycles but no adhesion was shown. - They have found out that the half bearing 1 according to the embodiment improves its heat resistant and its pressure resistant because the carbon fiber is mixed to the sliding
layer 2 and prevents the abrasion of the slidinglayer 2 as shown inFIG. 11 even under use conditions such that heavy load is applied for a long time. Further, since the half bearing 1 according to the embodiment has theuneven surface 6, which is formed on the surface of the slidinglayer 2, having the height higher than that of each of the comparison examples shown inFIGS. 6A and 7A at initial stage as shown inFIG. 5A , the oil film is more surely formed so that they have found out that the shape of the surface of the slidinglayer 2 in addition to the composition of the slidinglayer 2 prevents the abrasion of the slidinglayer 2. They also have found out that the uneven shape which becomes any oil reservoir to form the oil film remains, as shown inFIG. 5B , even under use conditions such that heavy load is applied for a long time. They further have found out that the half bearing 1 according to the embodiment prevents any abrasion of the slidinglayer 2 because the slidinglayer 2 is composed of polytetrafluoroethylene which has lower friction coefficient than that of Cu series alloy. - The half bearing according to the comparison example 1 indicated as shown in
FIG. 6A that the arithmetic mean roughness (Ra) before the test was 2.262 μm, the 10-point average roughness (Rz) before the test was 8.588 μm and the average spacing in roughness (Sm) before the test was 0.3299 mm. - As opposed to such a shape before the test, it indicated as shown in
FIG. 6B that the arithmetic mean roughness (Ra) after the test under the above-mentioned condition was 0.3373 μm, the 10-point average roughness (Rz) after the test was 1.479 μm and the average spacing in roughness (Sm) after the test was 0.1721 mm. - In the half bearing according to the comparison example 1, as shown in the microphotograph of
FIG. 9 , no adhesion was shown but the porous layer was exposed after 250 thousand cycles. They have found out that the half bearing according to the comparison example 1 has good slidability because lead (PB) is contained therein but the abrasion loss is large as shown inFIG. 11 so that there is a high probability of generating adhesion under use conditions in which that heavy load is applied for a long time. - The half bearing according to the comparison example 2 indicated as shown in
FIG. 7A that the arithmetic mean roughness (Ra) before the test was 2.299 μm, the 10-point average roughness (Rz) before the test was 8.798 μm and the average spacing in roughness (Sm) before the test was 0.3114 mm. - As opposed to such a shape before the test, it indicated as shown in
FIG. 7B that the arithmetic mean roughness (Ra) after the test under the above-mentioned condition was 0.5024 μm, the 10-point average roughness (Rz) after the test was 2.308 μm and the average spacing in roughness (Sm) after the test was 0.1212 mm. - In the half bearing according to the comparison example 2, as shown in the microphotograph of
FIG. 10 , no adhesion was shown after 250 thousand cycles. The uneven by the blasting process remained but the height of the uneven decreased as shown inFIG. 7B . Since the sliding layer composed of Cu—Sn series alloy is formed in the half bearing according to the comparison example 2, the abrasion is prevented as shown inFIG. 11 but the height of the uneven surface, shown inFIG. 7A , which is formable by the shot blasting process is lower than that of the sliding layer of the embodiment shown inFIG. 5A . Thus, they have found out that the embodiment and the comparison example 2 have the similar abrasion loss as shown inFIG. 11 but under the use conditions such that heavy load is applied for a long time, any uneven shapes, which becomes the oil reservoir that forms the oil film, remain, as shown inFIG. 5B , in the embodiment while any uneven shapes, which becomes the oil reservoir that forms the oil film, disappear, as shown inFIG. 7B , so that there is a high probability of generating the adhesion in the comparison example 2. - As results of the above, they have found out that the
porous layer 4 in the half bearing 1 is preferably composed of Cu—Sn series alloy having a particle size of 45 through 250 μm, in order to maintain the slidinglayer 2 under the use conditions such that heavy load is applied for a long time. - They have also found out that the sliding
layer 2 in the half bearing 1 is preferably composed ofresin material 5 including the polytetrafluoroethylene which has low friction factor and a carbon fiber which has good heat resistant and good pressure resistant. - Further, they have found out that the
uneven surface 6 of the slidinglayer 2 in the half bearing 1 preferably has surface roughness of 3.0 through 10.0 μm, more preferably, 6.0 through 10.0 μm, in the arithmetic mean roughness (Ra). - The present invention is applied to a sliding member used under the boundary lubrication in which the heavy load is applied and it is difficult to form any oil film.
- 1 . . . Half Bearing; 2 . . . Sliding Layer; 3 . . . Metal Substrate; 4 . . . Porous Layer; 5 . . . Resin Material; 6 . . . Uneven Surface; 6 a . . . Recess Potion
Claims (3)
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JP2012137800A JP5459356B2 (en) | 2012-06-19 | 2012-06-19 | Half bearing |
JP2012-137800 | 2012-06-19 | ||
PCT/JP2013/066720 WO2013191172A1 (en) | 2012-06-19 | 2013-06-18 | Half bearing |
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US20180163779A1 (en) * | 2015-06-23 | 2018-06-14 | Oiles Corporation | Sliding bearing |
US11338737B2 (en) * | 2018-12-07 | 2022-05-24 | Magna Exteriors, Inc. | Composite bushing within the arb pivot pin locations, integrated into automated running board |
US11976689B2 (en) * | 2019-06-12 | 2024-05-07 | Senju Metal Industry Co., Ltd. | Sliding member and bearing |
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WO2018181706A1 (en) * | 2017-03-30 | 2018-10-04 | Ntn株式会社 | Sintered bearing and method for manufacturing same |
CN110475982B (en) * | 2017-03-30 | 2021-05-07 | Ntn株式会社 | Sintered bearing and method for manufacturing same |
JP6917290B2 (en) * | 2017-12-12 | 2021-08-11 | オイレス工業株式会社 | Plain bearing |
WO2019117244A1 (en) * | 2017-12-15 | 2019-06-20 | 千住金属工業株式会社 | Sliding member and bearing |
JP7075251B2 (en) | 2018-03-22 | 2022-05-25 | 大同メタル工業株式会社 | Sliding member |
JP7344093B2 (en) * | 2019-11-07 | 2023-09-13 | 大同メタル工業株式会社 | sliding member |
JP2022157529A (en) * | 2021-03-31 | 2022-10-14 | 三菱重工業株式会社 | fluid film bearing |
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Also Published As
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JP5459356B2 (en) | 2014-04-02 |
EP2863080A1 (en) | 2015-04-22 |
CN104395626A (en) | 2015-03-04 |
US9393621B2 (en) | 2016-07-19 |
WO2013191172A1 (en) | 2013-12-27 |
EP2863080B1 (en) | 2016-04-13 |
EP2863080A4 (en) | 2015-05-27 |
CN104395626B (en) | 2016-03-09 |
JP2014001808A (en) | 2014-01-09 |
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